Compressor

ABSTRACT

A compressor includes a discharge chamber, a compression chamber, a partition wall, and a discharge reed valve. The partition wall is arranged between the discharge chamber and the compression chamber and includes a fixing surface that faces the discharge chamber. The partition wall includes a discharge port that can communicate the discharge chamber and the compression chamber. The discharge reed valve includes a fixed portion, an intermediate portion, and a valve portion. The partition wall includes a supporting portion, a receiving portion, and a main coupling portion. The supporting portion supports a central region of the valve portion. The receiving portion receives a distal region of the valve portion. The main coupling portion extends from the supporting portion to couple the supporting portion and the receiving portion in order to divide into two a distal discharging region of the discharge port.

TECHNICAL FIELD

The present invention relates to a compressor.

BACKGROUND ART

The following compressor is known (e.g., patent document 1). In thiscompressor, a valve plate is arranged between a discharge chamber and acompression chamber. A discharge port, which extends through the valveplate, can communicate the discharge chamber and the compressionchamber. A discharge reed valve, which is located in the dischargechamber, opens and closes the discharge port.

The discharge reed valve includes a fixed portion, which is fixed to afixing surface that is a surface of the valve plate at a side facing thedischarge chamber, an intermediate portion, which extends toward adistal side along a longitudinal direction from the fixed portion andcan be lifted, and a valve portion, which extends toward the distal sidealong the longitudinal direction from the intermediate portion to openand close the discharge port. An annular groove that surrounds theentire circumference of the discharge port is arranged in the fixingsurface. A portion of the fixing surface between the discharge port andthe annular groove forms a valve seat surface that is flush with theportion of the fixing surface outward from the annular groove. In astate in which the discharge reed valve is closing the discharge port, adistal part of the valve portion extends beyond the valve seat surfacein the longitudinal direction.

In this type of compressor, it is ideal that the discharge portimmediately opens at the moment the difference between the pressure inthe discharge chamber and the pressure in the compression chamberexceeds zero. However, when lubricating oil is present like in an actualmachine, as shown in FIG. 23, an adhesive force S acts in a directioninhibiting the opening of a discharge reed valve 81. Thus, the dischargereed valve 81 does not open a discharge port 82 until a force F producedby the pressure difference prevails over the adhesive force S. In such asituation, a bore inner pressure (pressure in the compression chamber)is as shown in FIG. 24. Such a phenomenon in which the bore innerpressure becomes higher than the discharging pressure is referred to asover-compression and causes power loss. The adhesive force is producedby the oil film pressure of the lubricating oil. The oil film pressureis lower than the surrounding pressure when the discharge reed valve 81attempts to separate from the valve plate 27. The inventors refer tothis effect as a “negative squeeze effect”.

PATENT DOCUMENT

Patent Document 1: Japanese Laid-Open Patent Publication No. 11-117867

DISCLOSURE OF THE INVENTION

Such power loss leads to an increase in energy consumption. From thestandpoint of reducing energy consumption, it is desirable that thepower loss be further decreased.

Further, in the compressor described above, the discharge reed valve maybe damaged, and it is desirable that the durability be improved.

It is an object of the present invention to provide a compressor thatcan further reduce power loss and exhibit higher durability.

In order to achieve the above object, the inventors have analyzed theconventional compressor in detail. As a result, the inventors have takennotice of the enlargement of the discharge port and the moment thedischarge reed valve closes.

More specifically, if the discharge port has, for example, a circularshape when viewed from above, a pressure receiving area of the valveportion that opens and closes the discharge port increases in proportionto the square of the diameter of the discharge port. Thus, the forceopening the discharge port increases when the discharge port isenlarged. In this case, the adhesive force of the lubricating oil thatinhibits the valve opening acts on the circumferential edge of thedischarge port and is thus only proportional to the diameter of thedischarge port. This decreases the adhesive force when the dischargeport is enlarged. Therefore, when the discharge port is enlarged,over-compression can be reduced, and power loss can be suppressed.

However, in the simulation conducted by the inventors, when thedischarge port was enlarged, a central region of the valve portion wasgreatly bent into the discharge port due to the force of inertia or thepressure difference of the compression chamber and the discharge chamber(hereinafter referred to as “pressure difference”) during a suctionstroke at the moment the discharge reed valve closes. Thus, fatiguefailure is apt to occur at the valve portion. In particular, thistendency is stronger when the compressor operates at high speeds. Thislowers the durability of the compressor.

In particular, in the simulation, at the valve portion, the strikingagainst the valve seat surface starts from the side of the intermediateportion, and a stress wave is propagated toward the distal side. Thus,if the valve portion of the discharge reed valve has a circular shapewhen viewed from above, the valve portion extending toward the distalside along the longitudinal direction bends like a whip and stronglystrikes the fixing surface. This is because the mass of the dischargereed valve increases toward the distal side along the longitudinaldirection, and a large force of inertia acts on the valve portion towardthe distal side in the longitudinal direction. This phenomenon becomesremarkable when the intermediate portion is rectangular with its longsides extending in the longitudinal direction and the valve portion iscircular having a diameter that is larger than or equal to the shortsides of the intermediate portion so that the discharge reed valvegreatly opens the discharge port.

In this manner, the inventors have completed the present invention.

One aspect of the present invention provides a compressor comprising adischarge chamber, a compression chamber, a partition wall, and adischarge reed valve. The partition wall is arranged between thedischarge chamber and the compression chamber and includes a fixingsurface that faces the discharge chamber. The partition wall includes adischarge port that can communicate the discharge chamber and thecompression chamber. The discharge reed valve has a length extendingalong a longitudinal direction, a distal end, and a basal end. Thedischarge reed valve includes a fixed portion, an intermediate portion,and a valve portion. The fixed portion is located at the basal end andfixed to the fixing surface. The intermediate portion extends from thefixed portion toward the distal end and is liftable relative to thefixing surface. The valve portion further extends from the intermediateportion toward the distal end and is capable of opening and closing thedischarge port. The partition wall includes a supporting portion, areceiving portion, and a main coupling portion. The supporting portionsupports a central region of the valve portion. The receiving portionreceives a distal region of the valve portion. The main coupling portionextends from the supporting portion to couple the supporting portion andthe receiving portion in order to divide into two a distal dischargingregion of the discharge port located at a distal side of the supportingportion in the longitudinal direction. The discharge port extendsthrough the partition wall so as to leave the supporting portion, thereceiving portion, and the main coupling portion in the partition wall.The receiving portion has a larger width than the supporting portion ina direction orthogonal to the longitudinal direction.

In the compressor of the present invention, when the force of inertia orthe pressure difference acts to greatly bend the central region of thevalve portion into the discharge port at the moment the discharge reedvalve closes the central region of the valve portion, the supportingportion supports the central region of the valve portion. Further, in apreferred manner, the supporting portion, the main coupling portion, andthe receiving portion support the valve portion, which strikes thefixing surface while bending like a whip toward the distal side alongthe longitudinal direction. This prevents fatigue failure at the valveportion.

Further, in the compressor of the present invention, the receivingportion has a larger width than the supporting portion in a directionorthogonal to the longitudinal direction. Thus, when the valve portionof the discharge reed valve strikes the receiving portion, thelubricating oil on the receiving portion reduces the striking force dueto the squeeze film effect so that only a small stress acts on the valveportion, and a large stress is not produced at the distal region of thevalve portion. This further prevents fatigue failure at the dischargereed valve, and the compressor can exhibit high durability. With thesqueeze film effect, when a gap between parallel surfaces decreases atthe velocity V, due to the viscosity of the fluid, the fluid resistsbeing pushed out of the gap and generates pressure (proportional toviscosity coefficient and velocity V).

In the compressor, due to the operations described above, the pressurereceiving area of the valve portion is increased, the force that opensthe discharge port is increased by increasing the port diameter, whilethe increase of the adhesive force of the lubricating oil inhibitingvalve opening is limited. Thus, over-compression can be decreased andpower loss can be suppressed.

Accordingly, the compressor can further reduce power loss and exhibithigher durability.

Further, in the compressor, discharging pulsation can be reduced bylimiting the opening delay of the discharge reed valve. This improvesthe quietness of the compressor. Further, in the compressor,over-compression is decreased by increasing the port diameter. Thus,exciting force, bearing load, piston side force (lateral force), and thelike have a tendency of decreasing. This reduces mechanical loss andsuppresses wear. As a result, power consumption can be decreased, andreliability can be improved.

Japanese Laid-Open Patent Publication No. 2009-235913 discloses acompressor including a supporting portion that divides an entire suctionport into two. However, in regard with the disclosed technique of thepublication, the present invention has a significant advantage in thatsuperior effects are obtained at the discharge side, which requirescapacities that can endure harsher conditions.

When the widths of the supporting portion, the main coupling portion,and the receiving portion are increased, fatigue failure of the valveportion can be prevented. In contrast, when the areas of the supportingportion, the main coupling portion, and the receiving portion areincreased, the area of the discharge port is decreased. Further, anincrease in the contact area of the supporting portion, the maincoupling portion, and the receiving portion increases adhesive force,and the discharge port thus cannot easily open. To resolve thesecontradicting problems, the present invention allows for selection ofthe suitable size and shape of the supporting portion, the main couplingportion, and the receiving portion.

Preferably, the partition wall includes a sub-coupling portion extendingfrom the supporting portion to divide at least into two a basaldischarging region of the discharge port located at a basal side of thesupporting portion in the longitudinal direction. The discharge portextends through the partition wall so as to leave the supportingportion, the receiving portion, the main coupling portion, and thesub-coupling portion in the partition wall.

In this case, the discharge port is divided into two or more portsegments by the supporting portion, the receiving portion, main couplingportion, and the sub-coupling portion. This increases the strength ofthe supporting portion, and the valve portion that bends like a whip caneasily be supported sequentially from the basal side toward the distalside in the longitudinal direction. Further, fatigue failure iseffectively prevented at the valve portion.

Preferably, the sub-coupling portion extends along the longitudinaldirection. The discharge port is divided into two port segments by thesub-coupling portion, the supporting portion, the main coupling portion,and the receiving portion.

In this case, the advantages in which fatigue failure at the valveportion is prevented and the discharge port easily opens are obtained.

Preferably, the sub-coupling portion, the supporting portion, the maincoupling portion, and the receiving portion have widths that increasetoward the distal side in the longitudinal direction.

In this case, the discharge port easily opens at a basal dischargingregion, the receiving portion receives a distal region of the valveportion in a preferred manner, and fatigue failure at the valve portioncan be further prevented.

Preferably, the sub-coupling portion includes a first sub-couplingportion, which extends along the longitudinal direction, a secondsub-coupling portion, which extends at an angle of 90° in a clockwisedirection from the main coupling portion, and a third sub-couplingportion, which extends along at an angle of 90° in a counterclockwisedirection from the main coupling portion. The discharge port is dividedinto four port segments by the first sub-coupling portion, the secondsub-coupling portion, the third sub-coupling portion, the supportingportion, the main coupling portion, and the receiving portion.

This also easily obtains the advantages in which fatigue failure of thevalve portion is prevented and the discharge port easily opens.

Preferably, the sub-coupling portion includes a first sub-couplingportion, which extends at an angle of 120° in a clockwise direction fromthe main coupling portion, and a second sub-coupling portion, whichextends at an angle of 120° in a counterclockwise direction from themain coupling portion. The discharge port is divided into three portsegments by the first sub-coupling portion, the second sub-couplingportion, the supporting portion, the main coupling portion, and thereceiving portion.

This also easily obtains the advantages in which fatigue failure of thevalve portion is prevented and the discharge port easily opens.

Preferably, the sub-coupling portion, the supporting portion, the maincoupling portion, and the receiving portion are flush with the fixingsurface.

This reduces machining costs.

Preferably, the sub-coupling portion, the supporting portion, the maincoupling portion, and the receiving portion include a recess that isrecessed from the fixing surface.

In this case, the contact area of the valve portion of the dischargereed valve and the sub-coupling portion, the supporting portion, themain coupling portion, and the receiving portion decreases, the adhesiveforce decreases, and the valve easily opens.

Preferably, the recess extends in a groove-shaped form along thelongitudinal direction.

In this case, the contact area is decreased. Further, the adhesive forceproduced by the negative squeeze effect when the valve opens isdecreased, and the valve easily opens.

Preferably, the recess extends in a groove-shaped form along the lateraldirection.

This decreases the contact area. Further, the amount of oil suppliedfrom the fixing surface to the sub-coupling portion, the supportingportion, the main coupling portion, and the receiving portion decreases,the adhesive force decreases, and the valve easily opens.

Preferably, the sub-coupling portion, the supporting portion, the maincoupling portion, and the receiving portion include a crowning.

In this case, the contact area of the valve portion of the dischargereed valve and the sub-coupling portion, the supporting portion, themain coupling portion, and the receiving portion decreases, the adhesiveforce decreases, and the valve easily opens.

Preferably, the valve portion is enlarged in a direction that differsfrom the longitudinal direction as compared with the intermediateportion.

In this case, enlargement of the discharge port and an increase in thepressure receiving area of the valve portion can easily be realized.Thus, the force that opens the discharge port can be further increased,and an increase in the adhesive force of lubricating oil that hindersvalve opening at the intermediate portion can be avoided. As a result,over-compression can be further reduced, and power loss can besuppressed. Further, in this case, the distal region of the valveportion can further easily bend like a whip and strongly strikes thefixing surface. Thus, the advantages of the supporting portion, the maincoupling portion, and the receiving portion become further prominent.

Preferably, the fixing surface includes a first groove portion, whichextends around the discharge port, and a valve seat surface, which islocated between the discharge port and the first groove portion. Thevalve portion can come into contact with the valve seat surface to closethe discharge port. The first groove portion extends to a rangeoverlapping the intermediate portion when viewing the discharge reedvalve from above in a state closing the discharge port.

In this case, the valve portion seals the discharge port with the valveseat surface in a preferred manner.

Preferably, the first groove portion is an annular groove that surroundsthe discharge port in a circumferential direction.

In this case, in a state in which the discharge reed valve closes thedischarge port, the intermediate portion is overlapped with an arcportion in the annular groove facing the basal side in the longitudinaldirection over a larger area. Thus, the area in which the fixing surfaceadheres to the intermediate portion is decreased by an amountcorresponding to the overlapping area.

Preferably, the first groove portion has a C-shaped form and surroundsthe discharge port in a circumferential direction excluding a portion atthe distal side in the longitudinal direction.

In this case, the distance between the two ends of the C-shaped grooveat the distal side in the longitudinal direction can be increased toeasily form the receiving portion between the two ends. Thus, when thevalve portion of the discharge reed valve strikes the receiving portion,the lubricating oil on the receiving portion reduces the striking force.Thus, only a small stress acts on the valve portion, and a large stressis not produced at the distal region of the valve portion. As a result,the compressor effectively prevents damage to the discharge reed valveand has a superior durability.

Preferably, the fixing surface includes a second groove portion, whichis located at the basal side of the discharge port in the longitudinaldirection, and a communication groove, which is located in a rangeoverlapped with the intermediate portion and which extends along thelongitudinal direction. The second groove portion extends across theintermediate portion in a lateral direction when viewing the dischargereed valve from above in a state closing the discharge port. Thecommunication groove communicates the first groove portion and thesecond groove portion.

Portions in the fixing surface other than the communication groove maybe a contact portion that contacts the discharge reed valve.

In this case, foreign substances are prevented from being caught by theintermediate portion in a state in which the discharge reed valve closesthe discharge port. Further, when the discharge reed valve opens, amultiphase jet flow including gas and lubricating oil blows away thelubricating oil, which exists between the intermediate portion and thefixing surface and thereby removes the oil film. The jet flow isdischarged outward in the lateral direction of the discharge reed valvethrough the communication groove and the second groove portion from thefirst groove portion. This blows away the lubricating oil collected inthe first groove portion, the lubricating oil collected between thefixing surface and the intermediate portion and the lubricating oilcollected in the second groove portion. Further, the communicationgroove decreases the area of contact between the fixing surface and theintermediate portion. Thus, the compressor advances the timing at whichthe fixing surface and the intermediate portion separate from eachother. This suppresses over-compression of the gas.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a cross-sectional view of a compressor according to a firstembodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view showing a state in which adischarge reed valve opens a discharge port in the compressor of FIG. 1.FIG. 3 is a plan view showing a valve plate and a discharge valve plate,which includes a plurality of discharge reed valves, in the compressorof FIG. 1.

FIG. 4 is an enlarged plan view showing a state in which the dischargereed valve closes the discharge port in the compressor of FIG. 1.

FIG. 5 is an enlarged cross-sectional view taken along line Z-Z of FIG.4 showing a state in which the discharge reed valve closes the dischargeport in the compressor of FIG. 1.

FIG. 6 shows the compressor of FIG. 1, in which part (A) shows a planview of the discharge port, and the like, part (B) shows a plan view ofa discharging region, and part (C) shows a cross-sectional view of asupporting portion.

FIG. 7 is a plan view of a discharge port and the like in a compressoraccording to a second embodiment of the present invention.

FIG. 8 is a plan view of a discharge port and the like in a compressoraccording to a third embodiment of the present invention.

FIG. 9 is a plan view of a discharge port and the like in a compressoraccording to a fourth embodiment of the present invention.

FIG. 10 is a cross-sectional view of a supporting portion correspondingto line A-A of FIG. 6 in a compressor according to a fifth embodiment ofthe present invention.

FIG. 11 is a cross-sectional view of a supporting portion correspondingto line B-B of FIG. 6 in a compressor according to a sixth embodiment ofthe present invention.

FIG. 12 is a cross-sectional view of a supporting portion correspondingto line B-B of FIG. 6 in a compressor according to a seventh embodimentof the present invention.

FIG. 13 is a cross-sectional view of a supporting portion correspondingto line A-A of FIG. 6 in a compressor according to an eighth embodimentof the present invention.

FIG. 14 is a cross-sectional view of a supporting portion correspondingto line A-A of FIG. 6 in a compressor according to a ninth embodiment ofthe present invention.

FIG. 15 is a cross-sectional view of a supporting portion correspondingto line B-B of FIG. 6 in the compressor according to the ninthembodiment of the present invention.

FIG. 16 shows a compressor according to a tenth embodiment of thepresent invention, in which part (A) shows a plan view of a dischargeport and the like, and part (B) shows a cross-sectional view of asupporting portion.

FIG. 17 is an enlarged plan view showing a state in which a dischargereed valve closes a discharge port in a compressor according to aneleventh embodiment of the present invention.

FIG. 18 is an enlarged cross-sectional view taken along line Y-Y of FIG.17 showing a state in which the discharge reed valve closes thedischarge port in the compressor of FIG. 17.

FIG. 19 is an enlarged plan view showing a state in which a dischargereed valve closes a discharge port in a compressor according to atwelfth embodiment of the present invention.

FIG. 20 is an enlarged plan view showing a state in which the dischargereed valve closes the discharge port in a compressor according to athirteenth embodiment of the present invention.

FIG. 21 is an enlarged plan view showing a state in which a dischargereed valve closes a discharge port in a compressor according to afourteenth embodiment of the present invention.

FIG. 22 is an enlarged plan view showing a state in which a dischargereed valve closes a discharge port in a compressor according to afifteenth embodiment of the present invention.

FIG. 23 is a cross-sectional view illustrating the adhesive force andthe like that act on the discharge reed valve.

FIG. 24 is a graph showing the relationship of the time and the boreinner pressure in a compressor.

DETAILED DESCRPTION OF THE PREFERRED EMBODIMENTS

First to fifteenth embodiments of the present invention will now bedescribed with reference to the drawings.

First Embodiment

A compressor of a first embodiment is a variable displacement type swashplate compressor. As shown in FIG. 1, the compressor is provided with acylinder block 1 including a plurality of cylinder bores 1 a. Thecylinder bores 1 a are concentrically arranged at equal angularintervals and extended parallel to each other. The cylinder block 1 isheld between a front housing 3, which is located in the front, and arear housing 5, which is located in the rear, and fastened by aplurality of bolts 7 in this state. A crank chamber 9 is formed in thecylinder block 1 and the front housing 3. The rear housing 5 includes asuction chamber 5 a and a discharge chamber 5 b.

The front housing 3 includes a shaft hole 3 a, and the cylinder block 1includes a shaft hole 1 b. A drive shaft 11 is supported in a rotatablemanner by a shaft seal 9 a and radial bearings 9 b and 9 c in the shaftholes 3 a and 1 b. A pulley or an electromagnetic clutch (not shown) isarranged on the drive shaft 11. A belt (not shown), which is driven byan engine of a vehicle, runs about the pulley or an electromagneticclutch pulley.

The drive shaft 11 is press-fitted to a lug plate 13, which is arrangedin the crank chamber 9. A thrust bearing 15 is arranged between the lugplate 13 and the front housing 3. The drive shaft 11 is inserted througha swash plate 17, which is arranged in the crank chamber 9, to supportthe swash plate 17. A link mechanism 19, which supports the swash plate17 in a tiltable manner, couples the lug plate 13 and the swash plate17.

Each cylinder bore 1 a accommodates a piston 21, which can reciprocatein the bore 1 a. A valve unit 23 is arranged between the cylinder block1 and the rear housing 5. As shown in the enlarged view of FIG. 2, thevalve unit 23 includes a suction valve plate 25, which is in contactwith a rear end face of the cylinder block 1, a valve plate 27, which isin contact with the suction valve plate 25, a discharge valve plate 29,which is in contact with the valve plate 27, and a retainer plate 31,which is in contact with the discharge valve plate 29. The retainerplate 31 also functions as a gasket. The suction valve plate 25, thevalve plate 27, the discharge valve plate 29, and the retainer plate 31are stacked in this order to form the valve unit 23.

As shown in FIG. 1, front and rear shoes 33 a and 33 b, which form apair, are arranged between the swash plate 17 and each piston 21. Eachpair of the shoes 33 a and 33 b convert the wobbling movement of theswash plate 17 into a reciprocating movement of the piston 21.

The crank chamber 9 and the suction chamber 5 a are connected by a bleedpassage 35 a, and the crank chamber 9 and the discharge chamber 5 b areconnected by an air supply passage (not shown). A displacement controlvalve (not shown) is arranged in the air supply passage. Thedisplacement control valve is formed so that it can vary the open degreeof the air supply passage in accordance with the suction pressure. Acondenser is connected by a pipe to the discharge chamber 5 b. Thecondenser is connected by a pipe to an evaporator via an expansionvalve, and the evaporator is connected by a pipe to the suction chamber5 a of the compressor. The cylinder bores 1 a, the pistons 21, and thevalve unit 23 form compression chambers 24.

A plurality of suction ports 23 a are formed in the valve plate 27, thedischarge valve plate 29, and the retainer plate 31 to communicate thesuction chamber 5 a and the compression chambers 24. The suction valveplate 25 includes a plurality of suction reed valves 25 a that open andclose the suction ports 23 a.

As shown in FIGS. 2 to 5, a plurality of discharge ports 23 b are formedin the suction valve plate 25 and the valve plate 27 to communicate thecompression chambers 24 and the discharge chamber 5 b.

As shown in part (A) of FIG. 6, the discharge port 23 b for eachcylinder bore la is divided into two port segments 231 and 232 by asupporting portion 27 t, a receiving portion 27 h, a main couplingportion 27 v, and a sub-coupling portion 27 w, which will be describedlater.

As shown in FIG. 2, a plurality of discharge reed valves 29 a are formedin the discharge valve plate 29 to open and close the port segments 231and 232. The retainer plate 31 includes a retainer 31 a that restrictsthe lift length of each discharge reed valve 29 a. In the presentexample, as shown in FIG. 3, the discharge valve plate 29 includes acircular portion and a plurality of (six in the present embodiment)extended portions, which extend radially outward in the radial directionfrom the circular portion. The extended portions form the discharge reedvalves 29 a that open and close the discharge ports 23 b.

As shown in FIGS. 4 to 6, a ring-shaped annular groove 27 a, whichsurrounds the entire circumference of the discharge port 23 b, isarranged in a fixing surface 27 f, which is the surface of the valveplate 27 at the side facing the discharge chamber 5 b. The annulargroove 27 a serves as a first groove portion of the present invention.In the fixing surface 27 f, a ring-shaped region located between thedischarge port 23 b and the annular groove 27 a forms a valve seatsurface (also referred to as eyeglass portion) 27 b that is flush with aportion of the fixing surface 27 f located outward from the annulargroove 27 a. In the compressor, the suction valve plate 25 and the valveplate 27 serve as a partition wall.

As shown in FIGS. 2 to 5, each of the six discharge reed valves 29 a hasa basal end and a distal end and includes a fixed portion 291 a, whichis positioned at the basal end and fixed to the fixing surface 27 f ofthe valve plate 27, an intermediate portion 292 a, which extends towardthe distal end along the longitudinal direction of the discharge reedvalve 29 a from the fixed portion 291 a and can be lifted, and a valveportion 293 a, which extends toward the distal end along thelongitudinal direction from the intermediate portion 292 a to open andclose the discharge port 23 b. In the present embodiment, thelongitudinal direction is a direction that is parallel to the fixingsurface 27 f and that extends in the radial direction of the drive shaft11. In FIG. 4, in particular, the longitudinal direction from the basalend toward the distal end of each discharge reed valve 29 a is indicatedby reference character D1, and the longitudinal direction from thedistal end toward the basal end of each discharge reed valve 29 a isindicated by reference character D2.

As shown in FIG. 4, when viewing the intermediate portion 292 a and thevalve portion 293 a from above, the intermediate portion 292 a has arectangular shape in which the long sides extend toward the distal sidein the longitudinal direction D1. The valve portion 293 a is a circleconcentric with the annular groove 27 a having the short side of theintermediate portion 292 a as the diameter. A diameter of the valveportion 293 a in a direction orthogonal to the longitudinal direction D1is greater than the diameter of the valve seat surface 27 b in thelongitudinal direction D1.

As shown in FIGS. 4 and 6, the valve plate 27 includes the supportingportion 27 t, which receives the central region of the valve portion 293a, the receiving portion 27 h, which receives the distal region of thevalve portion 293 a, the main coupling portion 27 v, which couples thesupporting portion 27 t and the receiving portion 27 h, and thesub-coupling portion 27 w, which extends from the supporting portion 27t. The valve portion 293 a is circular, and the central region of thevalve portion 293 a is thus a fixed range including the center of thevalve portion 293 a. The distal region of the valve portion 293 a is afixed range located at the distal side of the central region. As shownin part (B) of FIG. 6, the valve plate 27 includes a discharging regionA, through which the discharge port 23 b extends. The discharging regionA includes a semicircular distal discharging region A1 located at thedistal side in the longitudinal direction D1 and a semicircular basaldischarging region A2 located at the basal side in the longitudinaldirection D1. As shown in part (A) of FIG. 6, the supporting portion 27t is a fixed range including the center O of the discharging region A.The supporting portion 27 t is arranged to receive the central region ofthe valve portion 293 a, and the discharge port 23 b is located at theleft and right of the distal side and the left and right of the basalside in the longitudinal direction D1 as viewed from the supportingportion 27 t. The main coupling portion 27 v extends from the supportingportion 27 t to divide the distal discharging region A1 into two. Thesub-coupling portion 27 w divides the basal discharging region A2 intotwo. The discharge port 23 b extends through the valve plate 27 so as toleave the supporting portion 27 t, the receiving portion 27 h, the maincoupling portion 27 v, and the sub-coupling portion 27 w in the valveplate 27. The supporting portion 27 t, the receiving portion 27 h, themain coupling portion 27 v, and the sub-coupling portion 27 w arearranged in the valve plate 27 and thereby divide the discharge port 23b into two port segments 231 and 232.

The sub-coupling portion 27 w, the supporting portion 27 t, the maincoupling portion 27 v, and the receiving portion 27 h are in an I-shapedform extending toward the distal side in the longitudinal direction D1.As shown in part (C) of FIG. 6, the supporting portion 27 t, thereceiving portion 27 h, the main coupling portion 27 v, and thesub-coupling portion 27 w are flush with the fixing surface 27 f. Thesupporting portion 27 t, the receiving portion 27 h, the main couplingportion 27 v, and the sub-coupling portion 27 w are located between theport segments 231 and 232. The port segments 231 and 232, which areshaped in such a manner, are formed, for example, by punching andpressing the valve plate 27.

As shown in part (A) of FIG. 6, the supporting portion 27 t, the maincoupling portion 27 v, and the sub-coupling portion 27 w have the samewidth in a direction orthogonal to the longitudinal direction D1.However, the receiving portion 27 h has a larger width than thesupporting portion 27 t, the main coupling portion 27 v, and thesub-coupling portion 27 w. The port segments 231 and 232 have cornersthat are not pointed but slightly rounded due to accuracy limitations ofthe punching and pressing or the like.

As shown in FIGS. 2 to 5, a long groove 27 c is arranged in the fixingsurface 27 f at the basal side of the discharge port 23 b in thelongitudinal direction D1 extending across the intermediate portion 292a in its lateral direction. The long groove 27 c serves as a secondgroove portion of the present invention. As shown in FIG. 4, whenviewing the long groove 27 c from above, the shape of the long groove 27c is an oblong ellipse that is orthogonal to the longitudinal directionD1. The long groove 27 c is deeper than the annular groove 27 a.

In the above compressor, when the drive shaft 11 is driven and rotated,the lug plate 13 and the swash plate 17 are synchronously rotated withthe drive shaft 11, and the pistons 21 are reciprocated in the cylinderbores 1 a with a stroke corresponding to the tilt angle of the swashplate 17. Thus, refrigerant gas is drawn from the suction chamber 5 ainto each compression chamber 24 and compressed. Then, the refrigerantgas is discharged to the discharge chamber 5 b. The refrigerant gas thatundergoes compression in the compressor contains lubricating oil in theform of a mist. The lubricating oil collects on sliding and moving partssuch as the pistons 21, the shoes 33 a and 33 b, the swash plate 17, andthe like to suppress wear. The lubricating oil is also collected in theannular grooves 27 a and the long grooves 27 c.

In this state, as shown in FIG. 2, the discharge reed valve 29 a iselastically deformed at the intermediate portion 292 a due to thedifference between the pressure in the discharge chamber 5 b and thepressure in the compression chamber 24. This opens the discharge port 23b at the valve portion 293 a. As shown in FIG. 5, the valve portion 293a does not open the discharge port 23 b until the pressure differenceprevails over the adhesive force of the intermediate portion 292 a.

In this compressor, when the force of inertia or pressure differenceacts to greatly bend the central region of the valve portion 293 a intothe discharge port 23 b at the moment the discharge reed valve 29 acloses the discharge port 23 b, the supporting portion 27 t supports thecentral region of the valve portion 293 a. The sub-coupling portion 27w, the supporting portion 27 t, the main coupling portion 27 v, and thereceiving portion 27 h are in an I-shaped form extending along thelongitudinal direction D1. This increases the strength of the supportingportion 27 t, and the valve portion 293 a that strikes the fixingsurface 27 f while bending like a whip toward the distal side along thelongitudinal direction D1 can easily be supported sequentially from thebasal side toward the distal side in the longitudinal direction D1. Thisprevents fatigue failure at the valve portion 293 a.

In this compressor, in particular, when the valve portion 293 a of thedischarge reed valve 29 a strikes the receiving portion 27 h, thelubricating oil on the receiving portion 27 h reduces the striking forcedue to the squeeze film effect so that only a small stress acts on thevalve portion 293 a, and a large stress is not produced at the distalend of the valve portion 293 a. This further prevents fatigue failure atthe discharge reed valve 29 a, and the compressor can exhibit highdurability.

In the compressor, due to the operations described above, the pressurereceiving area of the valve portion 293 a is increased, the force thatopens the discharge port 23 b is increased, and the adhesive force ofthe lubricating oil inhibiting valve opening is reduced. Thus,over-compression can be decreased and power loss can be suppressed.

Accordingly, the compressor can further reduce power loss and exhibithigher durability.

In the compressor, discharging pulsation can be reduced by suppressingthe opening delay of the discharge reed valve 29 a. This improves thequietness of the compressor. Further, in the compressor, the peakpressure in the compression chamber 24 can be lowered. Thus, the maximumcompression load can be reduced, and the reliability can be increasedfor the thrust bearing 15, the surfaces of contact of the shoes 33 a and33 b and the pistons 21, the sliding surfaces of the shoes 33 a and 33 band the swash plate 17, and the like.

In the compressor, the annular groove 27 a is arranged in the fixingsurface 27 f, as shown in FIG. 4. Thus, the intermediate portion 292 aand an arc portion 27 g (shown in FIG. 4) of the annular groove 27 a areoverlapped over a wide range in a state in which the discharge reedvalve 29 a closes the discharge port 23 b. The overlapping area reducesthe area of contact between the fixing surface 27 f and the intermediateportion 292 a. This shortens opening delays of the discharge reed valve29 a.

Further, in the compressor, the long groove 27 c is arranged in thefixing surface 27 f. Thus, foreign substances are prevented from beingcaught by the intermediate portion 292 a in a state in which thedischarge reed valve 29 a closes the discharge port 23 b.

Second Embodiment

As shown in FIG. 7, in a compressor of a second embodiment, fourtriangular port segments 231 to 234 having a center angle ofapproximately 90 degrees are combined to form the discharge port 23 b.

The supporting portion 27 d, the main coupling portion 27 v, thereceiving portion 27 h, and first to third sub-coupling portions 27 w 1to 27 w 3 are formed in the valve plate 27. The first sub-couplingportion 27 w 1 extends along the longitudinal direction D1. The secondsub-coupling portion 27 w 2 extends at an angle of 90° in the clockwisedirection from the main coupling portion 27 v. The third sub-couplingportion 27 w 3 extends at an angle of 90° in the counterclockwisedirection from the main coupling portion 27 v. The first to thirdsub-coupling portions 27 w 1 to 27 w 3 are arranged between the portsegments 231 to 234. The other parts are the same as the compressor ofthe first embodiment.

This compressor also has the same advantages as the compressor of thefirst embodiment.

Third Embodiment

As shown in FIG. 8, in a compressor of a third embodiment, threetriangular port segments 231 to 233 having a center angle ofapproximately 120 degrees are combined to form the discharge port 23 b.

A supporting portion 27 e, the main coupling portion 27 v, the receivingportion 27 h, and the first and second sub-coupling portions 27 w 1, 27w 2 are formed in the valve plate 27. The first sub-coupling portion 27w 1 extends at an angle of 120° in the clockwise direction from the maincoupling portion 27 v. The second sub-coupling portion 27 w 2 extends atan angle of 120° in the counterclockwise direction from the maincoupling portion 27 v. The supporting portion 27 e, the main couplingportion 27 v, the receiving portion 27 h, and the first and secondsub-coupling portions 27 w 1 and 27 w 2 are arranged between the portsegments 231 to 233. The other parts are the same as the compressor ofthe first embodiment.

This compressor also has the same advantages as the compressor of thefirst embodiment.

Fourth Embodiment

As shown in FIG. 9, a compressor of a fourth embodiment includeshalf-moon shaped port segments 231 and 232. The sub-coupling portion 27w, a supporting portion 27 i, the main coupling portion 27 v, and areceiving portion 27 j have widths that increase toward the distal sidein the longitudinal direction D1. The other parts are the same as thecompressor of the first embodiment.

This compressor also has the same advantages as the compressor of thefirst embodiment.

The present invention drastically suppresses large bending of thecentral region of the valve portion 293 a into the discharge port 23 b.Thus, the valve portion 293 a does not have to entirely contact thesupporting portion, the receiving portion, the main coupling portion,and the sub-coupling portion. This allows the forms of fifth to tenthembodiments described below to be adopted.

Fifth Embodiment

As shown in FIG. 10, in a compressor of a fifth embodiment, a recess 27k is formed in a surface of the supporting portion 27 t or the like. Therecess 27 k is formed to be groove-shaped at the two lateral ends of thesupporting portion 27 t or the like. The other parts are the same as thecompressor of the first embodiment.

In this compressor, the contact area of the valve portion 293 a and thesupporting portion 27 t and the like is small. This reduces the adhesiveforce and facilitates valve opening. In this structure, the supportingportion 27 t or the like has a width that suppresses the contact area,and further, the adhesive force while maintaining the strength. Theother advantages are the same as the first embodiment.

Sixth Embodiment

As shown in FIG. 11, in a compressor of a sixth embodiment, a recess 28a is formed in a surface of the supporting portion 27 t or the like. Therecess 28 a is formed to groove-shaped along the longitudinal directionof the supporting portion 27 t or the like. The other parts are the sameas the compressor of the first embodiment.

In this compressor, the contact area is reduced and the adhesive forceproduced by the negative squeeze effect is reduced during valve opening.This facilitates valve opening. The other advantages are the same as thefirst embodiment.

Seventh Embodiment

As shown in FIG. 12, in a compressor of a seventh embodiment, narrowgroove-like recesses 27 m are formed in the two longitudinal ends of thesupporting portion 27 t or the like. The recesses 27 m extends along thelateral direction of the supporting portion 27 t or the like. The otherparts are the same as the compressor of the first embodiment.

In this compressor, the movement of lubricating oil is blocked betweenthe valve seat surface 27 b and the supporting portion 27 t or the likeby the recesses 27 m. This stops the supply of lubricating oil from thevalve seat surface 27 b to the supporting portion 27 t or the like,reduces the adhesive force that acts between the supporting portion 27 tor the like and the valve portion 293 a, and facilitates valve opening.The other advantages are the same as the first embodiment.

Eighth Embodiment

As shown in FIG. 13, in a compressor of an eighth embodiment, threenarrow groove-like recesses 27 n are located between recesses 27 s,which are arranged at the two ends, in the supporting portion 27 t orthe like. The other parts are the same as the compressor of the sixthembodiment.

In this compressor, the contact area of the supporting portion 27 t orthe like and the valve portion 293 a is reduced and the adhesive forceis reduced. This facilitates valve opening. The other advantages are thesame as the first embodiment.

Ninth Embodiment

As shown in FIG. 14 or 15, in a compressor of a ninth embodiment, acrowning 27 p is formed on the supporting portion 27 t or the like. Theother parts are the same as the compressor of the first embodiment.

In this compressor, the contact area of the valve portion 293 a and thesupporting portion 27 t or the like is reduced, the adhesive force isreduced, and valve opening is facilitated. The other advantages are thesame as the first embodiment.

Tenth Embodiment

As shown in FIG. 16, in a compressor of a tenth embodiment, a pluralityof recesses 27 q are formed by coining and then grinding the supportingportion 27 t or the like. The other parts are the same as the compressorof the first embodiment. This compressor also has the same advantages asthe compressor of the sixth embodiment.

Eleventh Embodiment

As shown in FIGS. 17 and 18, in a compressor of an eleventh embodiment,a communication groove 27 r, which extends toward the distal side in thelongitudinal direction D1, is formed in the fixing surface 27 f tocommunicate the annular groove 27 a and the long groove 27 c. Portionsof the fixing surface 27 f other than the communication groove 27 r forma contact portion 27 s that comes into contact with the discharge reedvalve 29 a. The contact portion 27 s is located at the two lateralssides of the communication groove 27 r in the fixing surface 27 f.Further, the contact portion 27 s is overlapped with the intermediateportion 292 a when the discharge reed valve 29 a is in state of closingthe discharge port 23 b as viewed from above. In the present example,the width of the communication groove 27 r is about 50% to 75% the widthof the intermediate portion 292 a. This ensures that the contact portion27 s supports the intermediate portion 292 a.

In the compressor, when the discharge reed valve 29 a opens, some of amultiphase jet flow including the refrigerant gas and the lubricatingoil blows away the lubricating oil, which exists between theintermediate portion 292 a and the fixing surface 27 f, and thereby themultiphase jet flow removes the oil film. The jet flow is dischargedoutward in the lateral direction of the discharge reed valve 29 athrough the communication groove 27 r and the long groove 27 c from theannular groove 27 a. This blows away the lubricating oil collected inthe annular groove 27 a, the lubricating oil accumulated between thefixing surface 27 f and the intermediate portion 292 a, and thelubricating oil collected in the long groove 27 c. The communicationgroove 27 r decreases the area of contact between the fixing surface 27f and the intermediate portion 292 a. Thus, the compressor furtheradvances the timing at which the fixing surface 27 f and theintermediate portion 292 a separate from each other. This suppressesover-compression of the refrigerant gas. The other advantages are thesame as the first embodiment.

Twelfth Embodiment

As shown in FIG. 19, in a compressor of a twelfth embodiment, the valveportion 293 a has a circular shape having a diameter that is greaterthan or equal to the short sides of the intermediate portion 292 a. Inother words, the valve portion 293 a is enlarged with respect to theintermediate portion 292 a in a direction differing from thelongitudinal direction D1. The other parts are the same as the firstembodiment.

In this case, enlargement of the discharge port 23 b and an increase inthe pressure receiving area of the valve portion 293 a can be easilyrealized. This further increases the force that opens the discharge port23 b, and the adhesive force of the lubricating oil that inhibits thevalve opening in the intermediate portion 292 a is prevented from beingincreased. As a result, over-compression can be further reduced, andpower loss can be suppressed in an ensured manner. In this case, thedistal end toward the distal side in the longitudinal direction D1 ofthe valve portion 293 a is more easily bent like a whip and thusstrongly strikes the fixing surface 27 f. Thus, the advantages of thesupporting portion 27 t or the like become more prominent. The otheradvantages are the same as the first embodiment.

Thirteenth Embodiment

As shown in FIG. 20, in a compressor of a thirteenth embodiment, thesupporting portion 27 i or the like of the fourth embodiment is used inlieu of the supporting portion 27 t or the like of the first embodiment,and a C-shaped groove 27 y is used in lieu of the annular groove 27 a ofthe first embodiment. The C-shaped groove 27 y also serves as the firstgroove portion of the present invention. The C-shaped groove 27 y, whichhas an arcuate shape concentric with the center O, is formed in thefixing surface 27 f and surrounds the discharge port 23 b in thecircumferential direction excluding the distal side in the longitudinaldirection D1. A region of the fixing surface 27 f sandwiched by theopposing ends of the C-shaped groove 27 y defines a receiving portion 27j and a receiving portion 27 z. The other parts are the same as thefirst embodiment.

In this case, the distance between the opposing ends of the C-shapedgroove 27 y can be increased to facilitate formation of the receivingportions 27 j and 27 z that are enlarged in the lateral direction of thesupporting portion 27 i as compared with other parts of the supportingportion 27 i (parts of the supporting portion 27 i other than thereceiving portions 27 j and 27 z). Thus, when the valve portion 293 astrikes the receiving portions 27 j and 27 z, the lubricating oil on thelarge receiving portions 27 j and 27 z ensure that the striking force isdecreased. Thus, only a small stress acts on the valve portion 293 a,and a large stress is not produced at the distal end of the valveportion 293 a. As a result, this compressor also effectively preventsdamage to the discharge reed valve 29 a and obtains superior durability.The other advantages are the same as the first embodiment.

Fourteenth Embodiment

As shown in FIG. 21, in a compressor of a fourteenth embodiment, thesupporting portion 27 i or the like of the fourth embodiment is used inlieu of the supporting portion 27 t or the like of the first embodiment,and two first groove portions 27 x are used in lieu of the annulargroove 27 a of the first embodiment. The first groove portions 27 x,which are arc-shaped and concentric with the center O, are formed in thefixing surface 27 f and surround the discharge port 23 b from the leftand the right excluding the distal side and the basal side in thelongitudinal direction D1. A region sandwiched by the opposing ends onthe distal side in the longitudinal direction D1 in the first grooveportions 27 x define a receiving portion 27 j and a receiving portion 27z in the fixing surface 27 f. A region sandwiched by the opposing endsat the basal side in the longitudinal direction D1 in the first grooveportions 27 x defines a basal side receiving portion 274 in the fixingsurface 27 f. The other parts are the same as the first embodiment.

In this case, the distance between the opposing ends of the first grooveportions 27 x at the distal side in the longitudinal direction D1 isincreased to facilitate formation of the receiving portions 27 j and 27z that are larger than other portions. Thus, in the same manner as thecompressor of the thirteenth embodiment, a large stress is not producedat the distal end of the valve portion 293 a. Further, in thecompressor, when the intermediate portion 292 a of the discharge reedvalve 29 a strikes the basal side receiving portion 274, only a smallstress acts on the intermediate portion 292 a due to the large basalside receiving portion 274. As a result, this compressor alsoeffectively prevents damages to the discharge reed valve 29 a andobtains superior durability. The other advantages are the same as thefirst embodiment.

Fifteenth Embodiment

As shown in FIG. 22, in a compressor of a fifteenth embodiment, only asupporting portion 27 u, the main coupling portion 27 v, and thereceiving portion 27 h are arranged in the valve plate 27, and aU-shaped discharge port 23 b is used. Thus, the supporting portion 27 ucan receive the central region of the valve portion 293 a in the samemanner as the supporting portion 27 t of the first embodiment. The otherparts are the same as the first embodiment.

In this case as well, the same advantages as the first embodiment areobtained.

The present invention has been described with the first to fifteenthembodiments. However, the present invention is not limited to the firstto fifteenth embodiments and may be modified within the scope of theinvention.

For instance, the supporting portion or the like may be formed in thevalve plate 27 or by a discrete member such as a damping steel plate orthe like.

The long groove 27 c is deeper than the annular groove 27 a in the firstembodiment, and the annular groove 27 a, the long groove 27 c, and thecommunication groove 27 r are formed with the same depth in the eleventhembodiment. However, the depths are not limited in such a manner.

The recesses 27 k, 27 a, 27 m, 27 s, and 27 q and the crowning 27 pdescribed in the fifth to tenth embodiments may be arranged in only thesupporting portion 27 t or may be arranged extending across thesupporting portion 27 t, the main coupling portion 27 v, and thesub-coupling portions 27 w, and 27 w 1 to 27 w 3.

INDUSTRIAL APPLICABILITY

The present invention may be applied to a vehicle air conditioningsystem.

1. A compressor comprising: a discharge chamber; a compression chamber;a partition wall arranged between the discharge chamber and thecompression chamber and including a fixing surface that faces thedischarge chamber, wherein the partition wall includes a discharge portthat can communicate the discharge chamber and the compression chamber;and a discharge reed valve having a length extending along alongitudinal direction, a distal end, and a basal end, wherein thedischarge reed valve includes a fixed portion located at the basal endand fixed to the fixing surface, an intermediate portion extending fromthe fixed portion toward the distal end and being liftable relative tothe fixing surface, and a valve portion further extending from theintermediate portion toward the distal end and being capable of openingand closing the discharge port, wherein the partition wall includes asupporting portion that supports a central region of the valve portion,a receiving portion that receives a distal region of the valve portion,and a main coupling portion that extends from the supporting portion tocouple the supporting portion and the receiving portion in order todivide into two a distal discharging region of the discharge portlocated at a distal side of the supporting portion in the longitudinaldirection, the discharge port extends through the partition wall so asto leave the supporting portion, the receiving portion, and the maincoupling portion in the partition wall, and the receiving portion has alarger width than the supporting portion in a direction orthogonal tothe longitudinal direction.
 2. The compressor according to claim 1,wherein the partition wall includes a sub-coupling portion extendingfrom the supporting portion to divide at least into two a basaldischarging region of the discharge port located at a basal side of thesupporting portion in the longitudinal direction, and the discharge portextends through the partition wall so as to leave the supportingportion, the receiving portion, the main coupling portion, and thesub-coupling portion in the partition wall.
 3. The compressor accordingto claim 2, wherein the sub-coupling portion extends along thelongitudinal direction; and the discharge port is divided into two portsegments by the sub-coupling portion, the supporting portion, the maincoupling portion, and the receiving portion.
 4. The compressor accordingto claim 3, wherein the sub-coupling portion, the supporting portion,the main coupling portion, and the receiving portion have widths thatincrease toward the distal side in the longitudinal direction.
 5. Thecompressor according to claim 2, wherein the sub-coupling portionincludes a first sub-coupling portion, which extends along thelongitudinal direction, a second sub-coupling portion, which extends atan angle of 90° in a clockwise direction from the main coupling portion,and a third sub-coupling portion, which extends along at an angle of 90°in a counterclockwise direction from the main coupling portion, and thedischarge port is divided into four port segments by the firstsub-coupling portion, the second sub-coupling portion, the thirdsub-coupling portion, the supporting portion, the main coupling portion,and the receiving portion.
 6. The compressor according to claim 2,wherein the sub-coupling portion includes a first sub-coupling portion,which extends at an angle of 120° in a clockwise direction from the maincoupling portion, and a second sub-coupling portion, which extends at anangle of 120° in a counterclockwise direction from the main couplingportion, and the discharge port is divided into three port segments bythe first sub-coupling portion, the second sub-coupling portion, thesupporting portion, the main coupling portion, and the receivingportion.
 7. The compressor according to claim 2, wherein thesub-coupling portion, the supporting portion, the main coupling portion,and the receiving portion are flush with the fixing surface.
 8. Thecompressor according to claim 2, wherein the sub-coupling portion, thesupporting portion, the main coupling portion, and the receiving portioninclude a recess that is recessed from the fixing surface.
 9. Thecompressor according to claim 8, wherein the recess extends in agroove-shaped form along the longitudinal direction.
 10. The compressoraccording to claim 8, wherein the recess extends in a groove-shaped formalong the lateral direction.
 11. The compressor according to claim 2,wherein the sub-coupling portion, the supporting portion, the maincoupling portion, and the receiving portion include a crowning.
 12. Thecompressor according to claim 1, wherein the valve portion is enlargedin a direction that differs from the longitudinal direction as comparedwith the intermediate portion.
 13. The compressor according to claim 1,wherein the fixing surface includes a first groove portion, whichextends around the discharge port, and a valve seat surface, which islocated between the discharge port and the first groove portion, thevalve portion can come into contact with the valve seat surface to closethe discharge port, and the first groove portion extends to a rangeoverlapping the intermediate portion when viewing the discharge reedvalve from above in a state closing the discharge port.
 14. Thecompressor according to claim 13, wherein the first groove portion is anannular groove that surrounds the discharge port in a circumferentialdirection.
 15. The compressor according to claim 13, wherein the firstgroove portion has a C-shaped form and surrounds the discharge port in acircumferential direction excluding a portion at the distal side in thelongitudinal direction.
 16. The compressor according to claim 1, whereinthe fixing surface includes a second groove portion, which is located atthe basal side of the discharge port in the longitudinal direction, anda communication groove, which is located in a range overlapped with theintermediate portion and which extends along the longitudinal direction,the second groove portion extends across the intermediate portion in alateral direction when viewing the discharge reed valve from above in astate closing the discharge port, and the communication groovecommunicates the first groove portion and the second groove portion.